CN116292286B - Screw rotor molded line for high-flow high-pressure differential compression - Google Patents
Screw rotor molded line for high-flow high-pressure differential compression Download PDFInfo
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- CN116292286B CN116292286B CN202211486765.1A CN202211486765A CN116292286B CN 116292286 B CN116292286 B CN 116292286B CN 202211486765 A CN202211486765 A CN 202211486765A CN 116292286 B CN116292286 B CN 116292286B
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- 238000007906 compression Methods 0.000 title claims abstract description 24
- 230000006835 compression Effects 0.000 title claims abstract description 23
- 238000013461 design Methods 0.000 claims abstract description 14
- 239000007789 gas Substances 0.000 claims description 19
- 239000001307 helium Substances 0.000 claims description 14
- 229910052734 helium Inorganic materials 0.000 claims description 14
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 claims description 14
- RWSOTUBLDIXVET-UHFFFAOYSA-N Dihydrogen sulfide Chemical compound S RWSOTUBLDIXVET-UHFFFAOYSA-N 0.000 claims description 5
- 229910000037 hydrogen sulfide Inorganic materials 0.000 claims description 5
- 230000005540 biological transmission Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 description 15
- 238000012545 processing Methods 0.000 description 8
- 239000001257 hydrogen Substances 0.000 description 7
- 229910052739 hydrogen Inorganic materials 0.000 description 7
- 238000003754 machining Methods 0.000 description 7
- 238000005516 engineering process Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 150000002431 hydrogen Chemical class 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- 239000000243 solution Substances 0.000 description 4
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 238000009413 insulation Methods 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 238000012360 testing method Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 238000012512 characterization method Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- -1 freon Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- QQONPFPTGQHPMA-UHFFFAOYSA-N propylene Natural products CC=C QQONPFPTGQHPMA-UHFFFAOYSA-N 0.000 description 1
- 125000004805 propylene group Chemical group [H]C([H])([H])C([H])([*:1])C([H])([H])[*:2] 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Theoretical Computer Science (AREA)
- Computational Mathematics (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The application relates to the field of energy power, in particular to a screw rotor molded line for high-flow high-pressure difference compression, wherein the tooth ratio of an asymmetric male rotor and an asymmetric female rotor is 5:7; the rotor molded line is designed to be a curve comprising a plurality of sections of continuous conductive elliptical arcs, quadratic curves and circular arc envelope curves; the curve curvature in different sections of the screw rotor molded line is determined by combining the actual working pressure state between rotor teeth, so that the workability of the precise molded line is realized, and the meshing gap is reduced to improve the volumetric efficiency. The integral molded line adopts a hydrodynamic design, has no common points, straight lines and cycloids in the traditional molded line, avoids the connection similar to sharp points, and solves the reliability problems of rotor rigidity, rotor dynamics and the like caused by high linear speed of a rotor under a high-flow working condition.
Description
Technical Field
The application relates to the field of energy power, in particular to a screw rotor molded line for high-flow high-pressure difference compression.
Background
A twin screw compressor is a positive displacement compressor in which compression of gas is achieved by a pair of intermeshing rotors. Tooth profile is also known as profile wire and is the core technology of twin-screw compressors. The screw compressor technology was further in advance, and the efficiency was refreshed each time, mainly from the molded line technology innovation. Rotor profile is the most core and fundamental technology of twin screw compressor technology. The end surface molded line of the rotor is composed of a plurality of sections of different curves, and each pair of mutually meshed spiral teeth are matched to complete the gas compression cycle. The rotor end face profile substantially determines the efficiency and rotor stability performance of the compressor.
The rotor profile develops from an initial symmetrical circular arc to an asymmetric complex geometric profile of today. The development direction of tooth shape is to increase the area utilization coefficient by increasing the tooth height radius, thinning the tooth thickness and the like. The traditional molded lines widely adopted in the fields of air compressors, refrigeration compressors and the like cannot meet the requirements of high-efficiency compression of small molecular weight gases such as helium, hydrogen and the like, and also cannot meet the requirements of screw operation reliability under high-capacity heavy-load working conditions. The profile affects not only whether the rotor can mesh correctly, but also internal leakage between different pressures in the axial and transverse directions, thus affecting the efficiency of the compressor. The hydrodynamic design of different curves not only affects the resistance loss of gas flow, but also affects the stirring work loss of cooling oil, so that the molded line design accords with the hydrodynamic rule and reduces the viscosity loss.
The mathematical geometry of the molded line in theory can be used for smooth transition and various shapes. However, the design of the molded line needs to consider the machinability of the theoretical molded line, and whether the theoretical shape is realized with enough machining precision in the existing industrial level or not often restricts the actual performance of the compressor when the low molecular weight gas is compressed. Particularly for any leaked medium, finer meshing clearance is required to reduce internal leakage loss, and the required molded line has stronger workability to ensure machining accuracy. Meanwhile, the specific geometric structure of the molded line needs to consider the actual conditions of the compression working medium and the operation working condition, and a large amount of test data are accumulated and continuously optimized.
In the current screw compressor field, asymmetric molded lines are used as traditional mainstream molded lines for industrial application, such as Atlas-X (4:6) molded lines, sigma (5:6) molded lines, GHH (5:6) molded lines, SRM-D (5:6) molded lines, GHH (5:6) molded lines, hitachi (5:6) molded lines, and the like.
thecharacteristics,advantagesanddisadvantagesofthetraditionalmoldedlinesaredescribedbytakingtheSRM-Dmoldedlinesasexamples,andthetraditionalmoldedlinesaredevelopedonthebasisoftheSRM-Amoldedlines. theSRM-Amoldedlineadoptsfivetypesofcombinationsofpoint-cycloid,straightline-cycloid,pintootharcpairs,oppositerollingarcpairsandarc-arcenvelopelines. And the tooth curves of the SRM-D molded lines are circular arcs and envelope curves thereof, as shown in table 1 and fig. 1, the curved surface-to-curved surface sealing is realized between the rotors, the transverse leakage through the contact line is reduced, the processing performance is improved, and the processing by adopting a hobbing method is facilitated. Table 2 summarizes the comparison between the specific compositional features of conventional molded lines.
TABLE 1 characterization of SRM-D molded lines
| Female rotor | Sun rotor | Meshing line | Female rotor | Sun rotor | Meshing line |
| Arc AB | Envelope line KL | 12 | Arc FG | Envelope PQ | 56 |
| Envelope line BC | Circular arc LM | 23 | Envelope curve GH | Arc QR | 67 |
| Arc CE | Circular arc MO | 34 | Circular arc HI | Envelope line RS | 71 |
| Envelope line EF | Arc OP | 45 | Arc IJ | Arc ST | 1 |
TABLE 2 characterization comparison of conventional molded lines
Besides the fact that the meshing gap is larger, the rotor molded line of the air compressor or the refrigeration compressor is not suitable for compressing small molecular weight gas, and the tooth shape is in transition due to more turning, when working media (such as helium) with larger cooling insulation indexes or high capacity working conditions (the linear speed of the rotor is increased), more oil injection quantity is needed, efficiency is reduced due to the increase of stirring oil work loss of the traditional molded line, and the high power consumption and the large noise of the compressor are shown.
In the design concept represented by the air screw compressor, the reliability is generally improved by reducing the rotating speed of a rotor according to the traditional rotor line design principle, but the reliability is greatly reduced in the case of high power capacity and high flow, and even the normal operation cannot be performed due to overlarge vibration.
On the other hand, as the nominal diameter of the rotor increases, in order to achieve high precision in machining precision molded lines such as compressed helium, it is necessary to consider the workability of the molded lines. When helium and hydrogen are compressed, the machining precision of the traditional molded line cannot meet engineering requirements due to the fact that smaller meshing gaps are needed.
Disclosure of Invention
The embodiment of the application provides a screw rotor molded line for high-flow high-pressure difference compression, which at least solves the technical problems of efficiency reduction caused by working medium leakage and rotor dynamics stability reduction caused by high rotor linear speed in the existing method.
According to an embodiment of the present application, there is provided a screw rotor profile for high flow high differential pressure compression, designed by the steps of:
designing a screw rotor molded line into a curve comprising a plurality of sections of continuously-conductive elliptical arcs, quadric curves and circular arc envelope curves; the screw rotor molded line adopts a male-female rotor number 5:7 asymmetric streamline design;
the curvature of the curves in the different sections of the screw rotor profile is determined in combination with the actual working pressure conditions between the rotor teeth.
Further, the screw rotor molded lines are formed by smoothly transiting and tangently connecting elliptical curves and parabolic curves with different curvatures.
Further, the curvatures of the different sections of the screw rotor profile are adjusted according to the different air pressure profiles that exist during the interdental microcell compression.
Further, in a high-pressure area, the molded line of the screw rotor is relatively gentle; in the low pressure area, the curvature of the molded line curve is enlarged, and the tight engagement between the male rotor and the female rotor is ensured.
Further, the screw rotor profile is designed to be a curve comprising 7 sections of continuously conductive elliptical arcs, quadratic curves and circular arc envelopes.
Further, the meshing gap of the male and female rotors is 10-30 mu m.
Further, the mesh gap is controlled to 10-20 μm when helium is compressed.
Further, the rotor circumferential line speed is 30-75m/s.
Further, the applicable working medium of the screw rotor is helium, hydrogen sulfide, air and refrigerant.
Further, the screw rotor is suitable for working conditions: rotor length-diameter ratio is 1.0-1.75, air inlet pressure is 30kPa-500kPa, single-stage suction-exhaust pressure difference is 300kPa-2000kPa, single-stage air delivery quantity is 800m 3 /h-13000m 3 /h。
The screw rotor molded line for high-flow high-pressure difference compression in the embodiment of the application is designed to be a curve comprising a plurality of sections of continuous and conductive elliptic arcs, quadric curves and circular arc envelope curves; the curvature of the curves in the different sections of the screw rotor profile is determined in combination with the actual working pressure conditions between the rotor teeth. The integral molded line adopts a hydrodynamic design, has no common points, straight lines and cycloids in the traditional molded line, and avoids the connection similar to sharp points, so as to adapt to the reliability requirement of the rotor caused by high linear speed under the high-flow working condition.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application and do not constitute a limitation on the application. In the drawings:
FIG. 1 is a diagram of the composition of each section of the SRM-D profile and the meshing of male and female rotors in a coordinate system according to the prior art;
FIG. 2 is a diagram of a global coordinate system and a local coordinate system for a medium-sized wire design according to the present application;
fig. 3 is a specific construction diagram of geometric curves of each section of the molded line according to the present application.
Detailed Description
In order that those skilled in the art will better understand the present application, a technical solution in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in which it is apparent that the described embodiments are only some embodiments of the present application, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present application without making any inventive effort, shall fall within the scope of the present application.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that the embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
The application mainly solves the problems of high linear speed (30-75 m/s) caused by large rotor diameter, increased internal leakage rate under differential pressure driving and larger rotor dynamics caused by heavy load rotor rigidity and dynamic balance of the screw compressor under the working conditions of large flow and high differential pressure. And more teeth are adopted and the tooth difference between the male rotor and the female rotor is increased in order to improve the rigidity and strength of the rotors while improving the meshing gap of the male rotor and the female rotor. The number and difference of teeth of the rotor are precisely designed, the utilization coefficient of the molded line area and the dynamic characteristics of the rotor (namely, the stability of the rotor) are improved, the vibration and noise are reduced in actual operation, the maintenance-free period is prolonged, and the like.
In order to realize the machinability of the precise streamline type molded line, the application provides a novel molded line with an asymmetric male-female rotor gear ratio of 5:7, and the nominal diameters of the rotors are consistent. In contrast to the conventional molded lines, better workability and rotor dynamics characteristics; because of the large number of teeth and large difference of teeth, the area utilization coefficient is improved, and the stability of the rotor and the volumetric efficiency of the compressor under heavy load working conditions (large pressure difference and large flow rate) are also improved.
The molded line is formed by smoothly transiting and tangently connecting a plurality of elliptic arcs with different curvatures, parabolas and other curves, the integral molded line adopts a fluid dynamics design, and has no points, straight lines and cycloids commonly used in the traditional molded line, so that the connection similar to sharp points is avoided, and the reliability requirement of the rotor caused by high linear speed under the condition of large flow is met. The curvatures of different sections are adjusted according to different air pressure distribution in the interdental infinitesimal compression process, and in a high-pressure area, the molded lines are relatively gentle and the machining precision is easier to realize; in the low pressure area, the curvature of the molded line curve is increased, the tight engagement between the male and female rotors can be ensured, and the engagement gap is controlled to be 10-25 mu m, so that the leakage of small molecular weight gases such as hydrogen, helium and the like is reduced.
The molded line is mainly applicable to: the air inlet pressure is 0.03-1.0MPa, and the single machine air delivery capacity is 800-13000m 3 And/h, rotor length-diameter ratio is 1.0-1.75; the working medium is hydrogen, helium, propylene, ammonia, freon, air and the like.
The novel molded line is further developed on the basis of the traditional molded line, is suitable for processing a rotor by a grinding method, and can achieve higher precision than rolling processing, thereby being better suitable for high-efficiency compression of small-molecular-weight gas and high-capacity and high-pressure-difference operation conditions. Sharp points, arcs of small radius, straight segments, etc. need to be avoided. The area utilization coefficient is improved by increasing the tooth height radius, thinning the tooth thickness and increasing the number of teeth. By further reducing the engagement gap and the leakage triangle, the internal leakage loss between the high and low pressures is reduced. The better fluid dynamics design reduces the loss of oil gas flowing work and further improves the efficiency and the reliability of the compressor.
The twin screw compressor drives the male and female rotors to move, and stability requires stable transmission between the male and female rotors, meaning that the rotors maintain a certain direction during operation, and if the torque direction changes, the rotors can collide on contact lines, thereby causing vibration, abrasion and noise. The SRM-D profile tooth shape is subject to such torque direction changes, particularly in large flow large diameter rotors. The novel line considers the factor when designing the tooth profile curve, thereby improving the running stability of the rotor.
In order to meet the working conditions of high flow and high pressure difference (the working medium leakage is more serious at the moment), the application changes the curvature (namely the geometric configuration) of the molded line according to the specific pressure distribution rule of the molded line of the rotor, and improves the processability and the processing precision of the molded line. The novel line has smaller meshing gap and additional oil flowing work loss, thereby improving compression efficiency, meeting the requirements of large-scale low-temperature engineering, and improving efficiency and stability in the fields of large-capacity commercial refrigerator compressors, process gas compressors and the like.
The molded line consists of 7 sections of curves such as continuous and conductive elliptic arcs, quadratic curves, circular arc envelope curves and the like; the curvature of the curve in the different sections, in combination with the determination of the actual working pressure state between the rotor teeth, is not solved by a separate mathematical engagement equation. Namely: in the opening direction of the molded line high-pressure end, the curvature of the molded line is reduced, the molded line tends to be flatter, and the machining precision is ensured; because the larger and steeper the curvature of the profile, the more difficult it is to control the machining accuracy. In the closing direction of the low-pressure end of the molded line, the molded line tends to be gentle, the molded line angle is properly increased, and the meshing gap of the male rotor and the female rotor is reduced, so that the internal leakage loss under high pressure difference is reduced. The technical scheme of the application comprises the following steps:
the number of teeth of the female rotor is increased by adopting the number of the male rotor and the female rotor of 5:7, so that the actual gas transmission capacity and the rotor rigidity (adapting to the gas force under high flow and high pressure difference) are improved; the increase of the gear ratio and the gear difference is that the rotor is stressed uniformly and the rigidity is 2-4 times of other gear ratios. The pressure difference between the primitive volumes is relatively reduced, so that the transverse gas leakage under the working condition of high pressure difference is reduced;
the meshing gap of the male rotor and the female rotor is 10-30 mu m, and the meshing gap is generally controlled to be 10-20 mu m when helium is compressed;
the method is mainly applicable to helium and hydrogen as working media, and can be popularized and applied to process gases such as hydrogen sulfide and the like and refrigerants such as air and freon;
the working conditions are as follows: rotor length-diameter ratio is 1.0-1.75, air inlet pressure is 30kPa-500kPa (absolute pressure), single-stage suction-exhaust pressure difference is 300kPa-2000kPa, single-station gas transmission quantity 800m 3 /h-13000m 3 /h；
Rotor circumferential line speed: 30-75m/s.
The technical scheme of the application is elaborated as follows:
line basic characteristics
The molded line consists of 7 sections of curves such as continuous and conductive elliptic arcs, quadratic curves, circular arc envelope curves and the like; the specific geometry of the curves in the different sections is determined by the pressure conditions in which the rotor is actually operating.
FIG. 2 is a global coordinate system and a local coordinate system used for the design of the molded lines of the present application; figure 3 is a geometric configuration of the profile of the present application.
The specific characteristics of each section of curve are given in the accompanying table 3 (the female rotor corresponds to 7 sections of curve and is the conjugate curve of each section of curve of the male rotor respectively).
TABLE 3 7 section Curve specific characteristics of this line
As shown in Table 3 and FIG. 3, the molded lines of the present application are composed of 7 continuously conductive curves and are uniquely defined by 21 characteristic parameters of A0, Z1, Z2, R1, R2, R3, R4, AA1, BB1, AA2, BB2, s, t, AY, φ 1, φ 2, α, φ 3, φ 4, φ 5, θ1.
Wherein A0 is the center distance between the male rotor and the female rotor;
z2 and Z1 are respectively the number of teeth of the male rotor and the female rotor;
r1, R2, R3 and R4 are arc radiuses of different segments (R2 and R4 are on the female rotor);
AA1, BB1, AA2 and BB2 are the major axis length and the minor axis length of elliptical arcs of different segments;
s and t are two parameters of a quadratic curve;
AY is the distance between the starting point A and the y axis;
phi 1, phi 2, alpha, phi 3, phi 4, phi 5, theta 1 are curve angle parameters of different segments.
The application is also characterized in that:
an asymmetric profile with a male-female rotor tooth ratio of 5:7;
the meshing clearance of the male rotor and the female rotor is 0.010-0.030mm;
rotor circumferential line speed: 30-75m/s, and also reduces the internal leakage rate of working medium;
the method is mainly applicable to helium as working medium, and can be popularized and applied to process gases such as hydrogen, hydrogen sulfide and the like, air and refrigerants;
the working conditions are as follows: the air inlet pressure is 30kPa-500kPa (absolute pressure), the single-stage air suction and exhaust pressure difference is 300kPa-2000kPa, and the single-stage air delivery quantity is 800m 3 /h-13000m 3 /h。
Second, embodiment line concrete coordinates
The present application gives the specific geometric coordinates of the molded lines by determining 21 parameters and the curvature and the meshing clearance values of each curve in the embodiment shown in table 4, namely the male rotor 514 set points and the female rotor 510 set points. The ratio of the teeth of the male rotor to the female rotor is 5:7, the meshing center distance is 164mm, and the contact line of the rotors is a spiral line formed by tangent points of pitch circles of the male rotor and the female rotor.
TABLE 4 example line coordinates (Unit: mm) of male and female rotors
The key points and the points to be protected of the application are at least:
1. the molded line of the application is formed by 7 sections of continuous conductive curves, and adopts asymmetric streamline molded lines with a male-female rotor ratio of 5:7;
2. the meshing gap of the male rotor and the female rotor is 10-30 mu m;
3. rotor linear speed: 30-75m/s;
4. rotor length-diameter ratio is 1.0-1.75;
5. the method is mainly applicable to helium as working medium, and can be popularized and applied to process gases such as hydrogen, hydrogen sulfide and the like, air and refrigerants;
6. the working conditions are as follows: air inlet pressure is 30kPa-500kPa (absolute pressure), single-stage suction-exhaust pressure difference is 300kPa-2000kPa, and single-stage air delivery quantity is 800m 3 /h-13000m 3 /h；
7. The embodiment line specific geometric curve (the male rotor 514 group points and the female rotor 510 group points) and the geometric characteristics thereof are enlarged and reduced in an equal proportion;
compared with the prior art, the application has the following advantages:
aiming at the problems of large meshing gap, reduced efficiency, vibration, noise increase and the like of the traditional screw molded lines under the large-flow working condition, the problems of poor rigidity, low strength, complex processing, high cost and the like of the male and female rotors, a novel rotor molded line suitable for high-speed operation is provided:
1. the rotor rigidity is 2-4 times of other gear ratios, so that the dynamic stability of the rotor is improved;
2. the geometric shape of the molded line is formed by 7 sections, and the curvature of each section curve is determined according to the actual pressure distribution, so that the processability and the processing precision of the molded line are improved;
3. the meshing gap is fine to 10-30 mu m, so that the volumetric efficiency is improved;
4. the peripheral line speed of the rotor is high: 30-75m/s; (the circumferential linear velocity of the traditional molded lines is generally 15-25 m/s);
5. the geometric characteristics of the molded line can still reduce the oil gas flowing work loss under the working condition of large flow and high pressure difference at high speed.
The application is detected by a test prototype, and the test result shows that the volumetric efficiency reaches 92.4%, the heat insulation efficiency reaches 84.9% and the isothermal efficiency reaches 61.4% under the rated working condition, and the main parameters are all the highest level (namely, the volumetric efficiency is 80.4-83%, the heat insulation efficiency is 72.6-78.1% and the isothermal efficiency is 52.9-56.7%) of the international product under the same working condition (power, mass flow and suction and exhaust pressure).
The modified design of the application comprises:
1) Intercepting tooth-shaped coordinate points and changing the ratio of male rotors to female rotors;
2) And scaling up or down the profile equally.
The foregoing embodiment numbers of the present application are merely for the purpose of description, and do not represent the advantages or disadvantages of the embodiments.
In the foregoing embodiments of the present application, the descriptions of the embodiments are emphasized, and for a portion of this disclosure that is not described in detail in this embodiment, reference is made to the related descriptions of other embodiments.
In the several embodiments provided in the present application, it should be understood that the disclosed technology may be implemented in other manners. The system embodiments described above are merely exemplary, and for example, the division of units may be a logic function division, and there may be another division manner in actual implementation, for example, multiple units or components may be combined or integrated into another system, or some features may be omitted, or not performed. Alternatively, the coupling or direct coupling or communication connection shown or discussed with each other may be through some interfaces, units or modules, or may be in electrical or other forms.
The units described as separate parts may or may not be physically separate, and parts displayed as units may or may not be physical units, may be located in one place, or may be distributed over a plurality of units. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.
In addition, each functional unit in the embodiments of the present application may be integrated in one processing unit, or each unit may exist alone physically, or two or more units may be integrated in one unit. The integrated units may be implemented in hardware or in software functional units.
The integrated units, if implemented in the form of software functional units and sold or used as stand-alone products, may be stored in a computer readable storage medium. Based on such understanding, the technical solution of the present application may be embodied in essence or a part contributing to the prior art or all or part of the technical solution in the form of a software product stored in a storage medium, comprising several instructions for causing a computer device (which may be a personal computer, a server or a network device, etc.) to perform all or part of the steps of the method of the various embodiments of the present application. And the aforementioned storage medium includes: a U-disk, a Read-only memory (ROM), a random access memory (RAM, randomAccessMemory), a removable hard disk, a magnetic disk, or an optical disk, or other various media capable of storing program codes.
The foregoing is merely a preferred embodiment of the present application and it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present application, which are intended to be comprehended within the scope of the present application.
Claims (8)
1. The screw rotor molded line for high-flow high-pressure difference compression is characterized by being designed by the following steps:
designing a screw rotor molded line into a curve comprising a plurality of sections of continuously-conductive elliptical arcs, quadric curves and circular arc envelope curves; the screw rotor profile adopts a male-female rotor tooth ratio of 5:7 asymmetric streamline design;
curve curvatures in different sections of the screw rotor molded line are determined by combining with the actual working pressure state between rotor teeth;
the molded line comprises a first arc, a first elliptic arc, a first arc envelope, a second arc envelope, a second elliptic arc and a quadratic curve which are connected in sequence.
2. The screw rotor profile for high flow high pressure differential compression of claim 1, wherein the curvature of the different sections of the screw rotor profile is adjusted based on the presence of different air pressure profiles during inter-tooth infinitesimal compression.
3. The screw rotor profile for high flow high pressure differential compression of claim 2, wherein the screw rotor profile is relatively gentle in the high pressure region; in the low pressure area, the curvature of the molded line curve is enlarged, and the tight engagement between the male rotor and the female rotor is ensured.
4. The screw rotor profile for high flow high pressure differential compression of claim 1, wherein the male and female rotor engagement gap is 10-30 μm.
5. The screw rotor profile for high flow high pressure differential compression according to claim 4, wherein the mesh gap is controlled to 10-20 μm when compressing helium.
6. The screw rotor profile for high flow high pressure differential compression of claim 4, wherein the rotor circumferential linear velocity is 30-75m/s.
7. The screw rotor profile for high flow high pressure differential compression of claim 1, wherein the screw rotor is adapted to be operated with helium, hydrogen sulfide, air.
8. The screw rotor profile for high flow high pressure differential compression of claim 1, which
Is characterized in that the screw rotor is applicable to working conditions: the length-diameter ratio of the rotor is 1.0-1.75, the air inlet pressure is 500kPa,
single stage suction and exhaust pressure difference 2000kPa, single stage gas transmission capacity 800m 3 /h-13000m 3 /h。
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| CN202211486765.1A CN116292286B (en) | 2022-11-25 | 2022-11-25 | Screw rotor molded line for high-flow high-pressure differential compression |
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| CN202211486765.1A CN116292286B (en) | 2022-11-25 | 2022-11-25 | Screw rotor molded line for high-flow high-pressure differential compression |
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| CN116292286A CN116292286A (en) | 2023-06-23 |
| CN116292286B true CN116292286B (en) | 2023-11-14 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN118030520B (en) * | 2024-03-04 | 2024-08-16 | 中国科学院理化技术研究所 | Single-stage high-pressure ratio streamline helium screw rotor |
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| US4576558A (en) * | 1984-04-07 | 1986-03-18 | Hokuetsu Industries Co., Ltd. | Screw rotor assembly |
| CN102606477A (en) * | 2012-03-29 | 2012-07-25 | 无锡五洋赛德压缩机有限公司 | Rotor profile of screw compressor |
| CN103291619A (en) * | 2013-07-03 | 2013-09-11 | 上海齐耀螺杆机械有限公司 | Double-screw compressor rotor molded line for oil injection |
| CN105041647A (en) * | 2015-08-19 | 2015-11-11 | 上海齐耀螺杆机械有限公司 | Tooth profile of double-screw compressor rotor |
| CN206668556U (en) * | 2017-03-27 | 2017-11-24 | 德耐尔节能科技（上海）股份有限公司 | A kind of double-screw compressor rotor flute profile |
| CN112302938A (en) * | 2019-07-30 | 2021-02-02 | 管大渊 | Energy-conserving efficient double screw compressor rotor molded lines |
| CN113294334A (en) * | 2021-06-07 | 2021-08-24 | 无锡锡压压缩机有限公司 | Helium screw compressor rotor |
-
2022
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| US4576558A (en) * | 1984-04-07 | 1986-03-18 | Hokuetsu Industries Co., Ltd. | Screw rotor assembly |
| CN102606477A (en) * | 2012-03-29 | 2012-07-25 | 无锡五洋赛德压缩机有限公司 | Rotor profile of screw compressor |
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| CN112302938A (en) * | 2019-07-30 | 2021-02-02 | 管大渊 | Energy-conserving efficient double screw compressor rotor molded lines |
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| CN116292286A (en) | 2023-06-23 |
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